Hydraulic coupling and change-speed gear



Sept. 30, K924. 11,51,36& H s. G. WINGQUIST HYDRAULIC COUPLING ANDCHANGE SPEED GEAR Filed July 14, 1922 2 Sheets-Sheet. 1

l i rz o 8 4 4 Vl/( 5 1 k E 1 v 24/ l g I 15 I 3 il 25 I 24 J IF\\ 6 Igwg I em. 30 1924., 135M368 s. G. WINGQUIST HYDRAULIC COUPLING ANDCHANGE SPEED GEAR 2 Sheets-Sheet 2 Patented Sept. 32, 1224.

SVEN GUSTAF WING'QUIST,

httttttt OF GOTTENBORG, SWEDEN.

HQEO

DRAULIC COUPLING AND CHANGE-SPEED GEAR.

Application filed July 14-,

To all whom it may concern.-

Be it known thatI, Sven GUSTAF WING- QUIST, a subject of the-King ofSweden, residing at Gottenborg, in the Kingdom of Sweden,-have inventednew and useful Improvements in Hydraulic Couplings and Change-SpeedGears, of which the following is a specification, reference being had tothe drawings accompanying and forming a part thereof.

This invention relates to a hydraulic coupling and change speed gearworking according to the differential principle and comprising a drivingrotor, a driven rotor and w a stator consisting of one or more elements.

The chief object of the present invention is to secure a smooth changefrom one transmission ratio to another and to utilize the energy ofmovement stored in the stator element or elements.

The invention consists, primarily, in the stator element or elementsbeing so arranged that, in direct drive that is to say when thecorresponding pump element is cut out, said 95 stator element orelements are automatically released and rotate with the driving rotor,whereas, when the corresponding pump element is thrown into action, saidstator'element or elements gradually obtain a decreased speed ofrotation and, thereby, im-

part their energy of movement to the driv ing rotor. The stator elementor elements are suitably arranged in such manner that, when theirabsolute speed is zero, they are automatically prevented from turning inthe direction opposite to the direction of rotation of the drivingrotor.

In the drawings, two forms of embodiment of a hydraulic couplin andchange speed gear according to the invention are illustrated by way ofexample. Fig. 1 is an axial section of the device. Fig. 2 is atransverse section taken along the line 2-2 of Fig. I viewed in thedirection of the arrows. Fig. 3 is a circular section taken along theline 3-3 ofFig. 1. Fig. 4 is a section along the line 4--4 of Figz 1viewed in the direction of the arrows. ig. 5 is a view similar to Fig.1, but showing a gear having two receiving pumps. Fig. 6 1s a transversesection taken along the ine tie-6 1922. Serial no. 575,027.

of Fig. 5 viewed in the direction of the arrows.

Referring to the drawings, the hydraulic coupling and change speed gearconsists of two pumps 2, 5 and 2, 7 of the ordinary sliding vane typehaving abutments 15, 16 and working faces 17, 18 respectively, the pump2, 5 being a delivery pump and pump 2, 7 a receiving pump. In thestructure disclosed, 1 is the driving shaft which is rigidl connected tothe outer casin 2, which functions as the driving rotor. ournaled in thesaid casing is a driven shaft 3, and keyed to the said shaft 3 is arotor 5 having radially movable vanes 4, said rotor constituting thedriven rotor. Within the casing 2 is, further, a stator 7 havingradially movable vanes 6, said stator bein keyed to a sleeve 8 adaptedto turn relatlvely to the driven shaft 3. Between the pressure chambers19 and 21 respectively of the two sliding vane pumps 2, 5 and 2, 7 is apassage 20 in which is a piston valve 9, actuated directly by the liquidin the pressure chamber 19 of the pump 2, 5 so that, at a certainpredetermined pressure in the said chamber, i. e. at a certainpredetermined turning moment of the driven shaft 3, said piston valveautomatically establishes communication between the pressure chambers ofthe pumps 2, 5 and 2, 7 so as to establish a transmission ratio,whereas, at an lower pressure in the chamber 19, said vs vs 9 is movedby spring action to a position in which the passa e between the pressurechambers is out o and a direct drive estab-- 'lished. In thev embodimentshown in Figs.

1 to 4, the sleeve 8 carrying the body porr tion 7 of the stator isprovided, at or near its outer end, with two pivoted arms 10, eachhaving a pawl 11 adapted to be brought, by the action of a spring 12,into engagement with corresponding recesses in a frame 13. When thesleeve rotates, the pawls 11 are disengaged from the recesses bycentrifugal force acting on the arms 10. As herein shown, the outer endof the stator sleeve 8 is formed as a flywheel 14 havin a relativelygreat mass, the energy of whic may be utilized in overcoming large orand den increases in load.

The device described operates as follows: Supposing the driving shaft 1with the casing 2 to be rotated in the direction of by dotted lines(Fig. 4), are caused by the centrifugal force to move outward, againstthe action of the s rings 12, into the positions, shown by ful lines. Ifthe load on the shaft 3 be then increased, the pressure in the pumelement 2, 5 is also increased, and the va ve 9 opens the passagebetween the pressure chambers 19 and 21, respectively of the pumps 2, 5and 2, 7 so as to establish a transmission ratio between the shafts.When the said passage is opened, a pressure will, obviously, arise inthe receiving pump 2, 7 and exert a braking action on the rotatingstator 7 so that the latter will gradually obtain a reduced speed and,through the medium of the uid, give off its energy 0 movement to thedriving rotor 2. Due to the gradually decreasing s eed of the stator,the coupling in or t e change from direct drive to a transmission ratiowill thus take place smoothly, and the energy stored in the stator 7 andthe flywheel mass 14 will be utilized for driving purposes instead ofbeing consumed in braking, in that, the braking action'of the stator 7will afford a reaction force on the abutment 16 which is thentransmitted through the rotor body 2 and the fluid in the chamber 19 tothe driven rotor 5, the fluid delivered from the delivery pump 2, 5 tothe receiving pump 2, 7 escapes through the chamber 22 and channel 23 tothe suction side 24 of chamber 19, a circulation of the fluid takingplace between the two pum s. The absolute speed of the stator 7 fina yapproaches zero, the centrifugal force on the arms 10 thus vanishes, andthe arms are caused by the action of the springs 12, to move inwardlyinto the positions shown by dotted lines (Fig. 4), in i which the pawls11 enga e the recesses in the frame 13. The stator ed from movin in thedirection opposite to the direction 0 rotation of the rotor 2, and theratio of gearing between the shafts 1 and 3 wi1 l thus be directldependent on the volumetric capacities o the two pumps. On the otherhand, if the load on the shaft 3 should decrease, the ressure in thedelivery pump 2, 5 will a so decrease, and, at a certain pressure,thevalve 9 will shut off ressure liqis thus preventthe passage 20between the pressure mamhere 19 and .21 respectively of the two pumps soas to establish direct drive. The

channel29, the chamber 22 and the channel 23 to the suction side 24 ofsaid delivery pump 2, 5. Secured to the free end of the sleeve-shapedportion 30 of the stator body 25 there is a pawl and ratchet device 31,similar to the device 10, 11 secured to the sleeve 8. Otherwise, thechange speed gear is identical with thatshown in Figs. 1 to 4,

the stator body 25 being, of course, rotatable with'relation to thesleeve 8 carrying .the stator 7.

' Also the action of the change speed gear according to Figs. 5 and 6 isidentical with that above {described with the difference only that, ifthe valve 9 opens the passage 20 between the delivery pump 2, 5 and thefirst receiving pump 2, 7 at a certain pressure, the valve 28 will openthe passa e 27 between -.the delivery pump 2, 5 an the second receivingpump 2, 25 at a somewhat higher ressure, the stator bodies 7 and 25being ecked, independently.

The invention is, obviously, not limited to the forms .of embodimentshown in the drawin since various changes may be made t erein withoutdeparting from the spirit of the invention.

I claim:

1. A hydraulic coupling and change speed gear comprising a dehverytpumpand at least one, receiving pump an a valvecontrolled passage betweenthe delivery gum and the receivin pump, said hyrau ic coupling and cange speed gear comprising a driving rotor, a drlven rotor, and astator,one of said rotors being common to both the delivery pump and therecelving ump, means for automatiaclly releasing t e stator so as torotate freely with the common rotor, when the said valvecontrolledpassage is closed, and means for permitting the stator to. automaticallyobtain a adual1y, decreaseds eed of rotation, w on opemngsaid vave-controlled passage, so that the change from one step of coupling toanother will take place smoothly and the ener of movement stored in thestator will e utilized.

2. A hydraulic coupling and change speed gear according to claim 1,having means for automatically preventing the statorfrom turning in adirection opposite SEGBd-gGitI' according to claim 1, in which to thedirection of rotation of the common t e stator is provided with anadditional rotor. flywheel mass.

3. A hydraulic coupling and change 5. A hydraulic coupling and changespeed 5 speed gear according to claim 1, having a gear accordingto clalm1,wherein the pumps 15 ratchet device for automatically preventing areof the sliding vane type and are co-axithe stator from turning in adirection opp0- ally arranged.

site to the direction of rotation of the com- In testimony whereof Ihave signed my mon rotor. name.

1 4. A hydraulic coupling and change SVEN GUSTAF WINGQUIST.

